Multiplying machine



March 26, 1940. w. l... MAxsoN r AL MULTIPLYING MACHINE '7 Sheets-Sheet 1 Filed Nov. 30, 1936 Fia/'er J. McLaren.

ATTORNEYS March Z6, 1940. w.-|.. MAxsoN ET A1.

MULTIPLYING MACHINE Filed Nov. so. 193s `'r sheets-sheet 2 INVENTORS.

WIKI/lam L Maxson and Peer J. McLaren.

ATTORNEYS.

March 26, 1940. w 1 MAXSQN ET AL 2,194,477

MULTIPLYING MACHINE Filed Nov. 30. 1936 7 Sheets-Sheet 3 Ffq. 5.

L i ll/ IM'OM INVENTORS Wl 'm L, Ma/xson and Pe J. McLaren.

ATTORNEYS .March '26 1940. w L MAXSON Er AL 2,194,477

MULTIPLYING MACHINE Filed Nov, 3o, 195s 'rsneets-sneet 4 www /lzo

KBZ

7 Sheets-Sheet 5 w. L. MAXSON ET AL MULTIPLYING MACHINE Filed Nov. 30. 1936 March 26, E940.

Z6, 1940.. w, L. MAxsoN ET AL MULTIPLYING MACHINE Filed Nov. so, 19:56 7 sheets-sheet e INVENTORS W/l//am L. Maxon and Peer J. McLaren ATTORNEYS INVENTOR Wfl/fam L Maxsdh and Pere/ml. McLaren.

ATTORNEY.

atented Mar. 26, 1940 UNM Eo STATES PATENT MULTIPLYING MACHINE Application November 30, 1936, Serial No. 113,398

10 Claims.

This invention has to do with computing machines and more particularly with machines for multiplying numbers. It is adaptable, for example, for use in gasoline stations where the price to be charged a customer is computed by multiplying the price per gallon of gasoline by the number of gallons sold.

The primary object of the present invention is to provide a computing machine including revoluble multiplicand and multiplier input means, and registers directly responsive to the respective input means for showing the instantaneous values of the multiplicand and the multiplier as they change in value, together with product indicating means and transmission mechanism consisting exclusively of revoluble members whereby the multiplicand input means, the multiplier input means, and the product indicating means are geared together for causing the product indicating means, in response to the joint effect of the multiplier and multiplicand input means, to show the instantaneous values of the product continuously as the product changes in value.

The underlying principle of the\ computing mechanism of a preferred form of this invention is based upon two elementary formulas of algebra, namely, that the square of the sum of two quantities is equal to the sum of squares plus twice the product, and that the square of the difference of two quantities is equal to the sum of the squares minus twice the product. From these two results it is evident that if the square of the diierence be subtracted from the square of the sum the remainder will be four times the product of the original quantities, and hence that by merely dividing the remainder by four the product of the two quantities will be revealed.

The present invention utilizes this principle of securing a product by providing means for separately running in and indicating the numbers to be multiplied. The operating members are bothconnected to two trains of mechanism. The connections are such that the quantities are combined additively in one train of mechanism and subtractively in the other train of mechanism. Each of these trains operates a squaring gear so that the output of one train is the square 0 of the sum of the quantities and the output of the other is the square of the diierence. 'I'hese results are dierentially combined by further gearing to operate an indicator to show onequarter of their difference or, in other words, the true product of the original numbers. The division by 4 may, of course, occur at any point in the gear train or trains. If performed in advance of the squaring gears the division would be by 2 instead of 4.

It is desirable that the operator be not required to discriminate between the operating members as to which shall be used for the larger number and which for the smaller. In the train which deals with the sum of the numbers it would, of course, be immaterial which operating member runs in the larger number and which runs in the smaller number. In the other train, however, one of the numbers is added and one of the numbers is subtracted and if the operating members selected are such that the number subtracted is a larger number than the number added the difference would be negative. This situation is taken care of in accordance with the present invention by providing for a reversal of the driving train of the squaring gear at the zero point. With this provision the net result comes out right because the squares of the same absolute values whether positive or negative are the same.

A reversing mechanism is also provided in the additive train to take care of negative numbers.

In accordance with one embodiment of the invention three squaring gears are operated appropriately from the multiplicand and multiplier inputs so that their outputs are respectively the square of the multiplicand the square of the multiplier and the square of the sum of the multiplier and the multiplicand. The iirst two outputs are added together to secure the sum of the squares and this sum is then subtracted from the square of the sum of the multiplier and the multiplicand. 'I'he difference bearsv a known xed relation to the product of the multiplier and multiplicand so that through appropriate gearing the product indicator may be caused to correctly show the product.

In another embodiment of the invention thenecessity for reversing mechanism is obvlated by starting the follower of one of the squaring gears, i. e., the gear which is turned in proportion to the diierence of the multiplier and multiplicand, from a known position other than zero. Suitable compensation is provided, controlled by the magnitude of the diierence of the multiplicand and the multiplier, to eliminate the eilect of this false start upon the output.

In still another embodiment of the invention Y The means for securing a non-linear outputv from a linear input is not claimed per se but is claimed in our divisional application Serial gNo. 276,280, led May 29, 1939 for Functional apparatus. f

In the drawings illustrating the principle and one preferred embodiment of the invention,

Fig. 1 1s a fragmentary, perspective view illustrating the principal parts of the apparatus the fl reversing mechanism of the right hand train be- 5 tion illustrating the differential mechanism for differentially combining the squares;

Fig. 4 is a fragmentary sectional .detail view showing a portionof one of the squaring devices;

Fig. 5 is a fragmentary view in sectional elevafl tion showing details of a reversing clutch;

Fig. 6 is a fragmentary, diagrammatic, plan view showing a squaring gear and associated parts;

Fig. 7 is a perspective view, largely diagram- 5 matic, illustrating a further embodiment of the invention;

Fig. 8 is a view similar to Fig. 7 illustrating another embodiment;

Fig. 9 is a view similar to Fig. '7 illustrating still another embodiment; and

Fig. 10 is a purely diagrammatic view illustrating still another embodiment of the invention.

Before the parts are described in detail the major elements will be referred to for the purpose of following through the principle of the invention.

An operator, as handle I, is turned to run the multiplicand into a counter 2. Through suitable gearing this forward rotation of the handle I U runs a gear 3 of the sum train forward and also runs a gear 4 of a difference train forward. (The gear 4 is shown disconnected in Fig. 1, but it would be effective during the running in of a positive multiplicand.)

5 A second operating handle 5 is turned forward to run the multiplier into a counter 6. 'Ihis forward rotation of the operating member 5 acts through suitable gearing to run the gear 3 of the sum train forward and to run the gear 3 4 of the difference train backward.

The net result is that the gear 3 of the sum train is operated forward in proportion to the sum of the numbers indicated by the counters 2 and 6 and the gear 4 is operated forward in 5 proportion to the difference of the numbers indicated by the counters 2 and 6. If the difference is negative, however, the gear 4 is thrown out of operation at zero and the gear 4a is made effective.

) The gear 3 acts upon the squaring gear I to operate a gear 8 in proportion to the square of the sum of the numbers indicated by the counters 2 and 6, while the gear 4 acts through a squaring gear 9 to operate a gear I0 in proportion to the square of the difference of the numbers indicated by the counters 2 and 6. 'I'hrough differential gearing these operations of the gears 8 and I0 are differentially combined to operate a gear II which, in turn, drives a gear I2 for rotating a product indicating counter I3. The counter I3 indicates one-quarter of the dierence of the squares and hence the product of the numbers run into the counters 2 and 6.

The operating handle I is desirably fast upon g a shaft I4 which carries a bevelled gear I5 which acts on a bevelled gear I 6 for driving number wheels of the counter 2. The shaft I4 has fast upon it a gear I'I which meshes with a. gear I8 loose upon a shaft I9. The gear I8 has fast with it a bevelled 'f ar 20 which meshes with bevelled gears 2I a 22 of a differential train. A further gear 23 also loose upon the shaft I9 is driving from gears 2| and 22 through a bevel gear 23a. The gear 23 meshes with a gear 24 fast upon a shaft 25, the operating member 5 being fixed upon the shaft 25. Any suitable provision may be made for preventing retrograde rotation of the shafts I4 and 25 except at times when such rotation is desired for the purpose of setting the mechanism back to zero or of running in a number negatively. During the forward rotation of the operating member I the gear 24 may 'be assumed to be fixed. This prevents rotation of the gear 23 and hence compels the gears 2l and 22 to travel not only about their own axes but also about the axis of the shaft I3. The shafts 26 upon which the gears 2I and 22 are journalled are carried by a block 2l fixed to the shaft I9 so that the gears in travelling about the axis of the shaft cause the shaft to rotate. It will be seen that rotation of the operating handle l in a clockwise direction turns the gear I8 in a counter-clockwise direction and results in a turning of the shaft I9 in a counterclockwise direction and in proportion to the turning of the gear I8.

When the gear I'I is held stationary and the gear 24 is turned clockwise by the operating handle 5, the gear 23 is turned counter-clockwise and this also results in turning the shaft I9 counter-clockwise and in proportion to the turning of the gear 24. The numbers run into the counters 2 and 6 are, therefore, additively combined in the rotation of the shaft I9.

The rotation of the operating handle I is also run positively into a shaft 28 similar to the shaft I9. Clockwise rotation of the gear I'I drives a meshing gear 29 counter-clockwise and this, in turn, drives a gear 30 loose on the shaft 28 in a clockwise direction. A bevelled pinion 3| fast with the gear 30 acts upon differential pinions 32 and 33 which mesh with a pinion 34. The pinion 34 is loose on the shaft 28 but is fixed to a gear 35 which meshes with the gear 24. Assuming that the gear 24 and hence the gear 35 is held against rotation while the handle I is turned forward, the clockwise rotation of the gear 30 results in a rotation of the shaft 28 in clockwise direction in proportion to'the rotation of the gear 30.

When the gear 30 is held stationary, however, and the gear 24 is turned clockwise by operation of the member 5 the resulting counter-clockwise rotation of the gear 35 causes the shaft 28 to be turned counter-clockwise. As a result of this subtractive combining of the operating members I and 5 in their effect upon the shaft 28, the net rotation of the shaft 28 is proportional to the difference of the numbers indicated by the counters 2 and 6.

The shaft I9 has fast upon it a gear 36 which, through gears 31 and 38, drives a gear 39 fast on a clutch sleeve 40. The clutch sleeve 48 is rotatably mounted upon a shaft 4I which shaft carries the gear 3. Normally the clutch sleeve 40 drives the gear 3 which in turn drives the squaring gear 1.

The squaring gear l is a spiral gear having teeth 4I affixed to it so as to extend in a spiral path. The teeth 4I are uniformly spaced to mesh with and drive a crown gear 42 which .is

slidably mountedv upon a square shaft 43. The 'spiral gear acts both to rotate the crown gear 4upon the shaft 43 is, therefore, driven in proportion to the square of the rotation of the gear 3. Features of construction of the gears 1 and 9 will be described at a later point in this specication.

The other train of mechanism, in which the numbers are subtractively combined, comprises a gear 44 fast on the shaft 28 which, through similar mechanism, normally drives the gear I so that the rotation of the gear I0 is in proportion to the square of the rotation of the gear 4. This train of mechanism comprises gears 45 and 46, a gear 41 fast on a clutch sleeve 48, the gear 4, gears 4b and 4c, the squaring gear 9, a crown gear 49, and a square shaft 50, the gear I0 being fast upon the shaft 50. The clutch gears 39 and 41 are neutral at zero. They differ in the fact that the positive position of the gear 39 is down and the negative position is up, whereas the reverse condition holds true of gear 41.

The gears 8 and I0 are connected through differential mechanism to drive a gear II in opposite directions. Gears 8 and I0 mesh respectively with gears 52 and 53 (Figs. 1 and 3), both rotatably mounted upon a horizontal shaft 54. The gears 52 and 53, respectively, have fixed to them bevelled pinions 55 and 56, both of which pinions mesh with bevelled pinions 51 and 58. The pinions 51 and 58 are revolubly mounted upon a shaft 59 which comprises a central block portion 50 fixed to the shaft 54.

The operation of a differential gear of4 this kind is well understood. When the gears 52 and 53 turn at the same speed in opposite directions, the pinions 51, and 58 merely turn about the axis of shaft 59 without causing the shaft to change its angular position relative to the axis of the shaft 54. When the gears 52 and 53 are turned at the same speed in the same direction they cause the shaft 54 to turn in unison with themselves. When one of the gears 52, 53 is turned and the other is held stationary, the shaft 54 is caused to turn in the same direction as the gear which is turning but at half the rotary speed of the gear. The simultaneous turning of the gears 52 and 53 at different speeds either in the same or opposite directions has the same effect on shaft 54 as if the same turning movements were applied to the two gears successively, each being held stationary while the other is being turned.

When a number is run into the counter 2 through the handle I, the spiral gears 1 and 9 are turned in the direction to carry the crown gears 42 and 49 away from the centers of the spiral gears. This turns the bottom of the gear I0 away from the observer as seen in Fig. 1 and the bottom of the gear 8 toward the observer as seen in Fig. 1. The gears 52 and 53 are, therefore, operated in opposite directions so that the shaft 54, and hence the gears II and I2, remain stationary. The counter I3 therefore remains at zero. In the meantime if the number run into the counter 2 is called a, the crown gears 42 and 49 will both have been 'operated to positions on the spiral gears corresponding to a2. If now a number b, which is less than a, is run in by the handle the crown gear 42 will be moved further outward to a position corresponding to (a-l-b) 2. 'I'he additional rotation imparted to the gear 8 will be in a direction to drive the counter I3 forward and in an amount equal to and the additional rotation imparted to the gear 53 will be in a direction to drive the counter I3 forward and in an amount equal to az (a. by

'fI'he net result on the counter is obviously, thereore or ab.

The desired result having been indicated and utilized, the mechanism may all be set back to zero by turning the handles I and 5 backward until the counters 2 and 6 read zero.

Since the mechanism will frequently be employed, however, in a place like a gasoline iilling station where the price of gasoline (the multiplicand) remains the same for a considerable time, there is no occasion nor necessity for setting the counter 2 back to zero at all. It may be left standing at the current price per gallon of gasoline. The normal positions of the gears 42 and 49 will then correspond to the square of this price, but the indicator I3 will read zero so long as the counter 6 reads zero. The handle 5 may be replaced by gearing connecting the shaft 25 to the gasoline pump through suitable clutch mechanism which causes the shaft 25 to be rotated forward in proportion to the amount of gasoline delivered but which permits the shaft to be uncoupled from the pump for setting back to zero. Suitable mechanical or electrical means, such as a spring motor or an electromagnetically operated pawl and ratchet mechanism, may be provided, if desired, for turning the shaft 25 to set the counters 6 and I3 back to zero upon the mere pressing of a button or trip by the operator.

While the above description has been on the assumption that the handle I is operated first, the apparatus operates in the same manner if the handle 5 is operated first. Starting from a condition in which all the counters stand at zero the only difference would be that the clutch 48 would shift to its negative or down position immediately upon the beginning of the operation. The spiral gear 49 would be operated away from the center as before so that at the conclusion of the turning of the handle 5 both of the crown gears 49 and 42 wpuld stand at positions corresponding to the square of the number turned in. In view of the reverse connections as compared with the operation first described, the subsequent turning of the handle I would have precisely the same effect upon the gears 42 and 49, and the mechanism which they jointly control, as that described in the turning of the handle 5 after the handle I.

While it is immaterial which handle is used for running in the larger number and also immaterial which handle is operated first, for the purpose of explaining the function and operation of the reversing mechanism it will be assumed rst that both numbers are positive, that the smaller number is run in first by means of the -handle I, and that the operation is started with all counters standing at zero.

Immediately upon the beginning of the forward revolution of the handle I the clutch 48 is shifted up and the clutch 40 is shifted down by mechanism which will be described presently. As has already been explained the complete operation of the handle I will cause the gears 42 and 49 to stand at their positions corresponding to the square of the number run in by the handle I. Now as the larger number is run in by the handle 5 the gear 42 continues to move out and takes up a position corresponding to (cz-HD2. So long as the clutch 48 remains down, gear 49 moves in toward the center of the spiral gear 9 until .it reaches its original or zero position. At that point the clutch 48 is shifted upward so that the direction of drive of the spiral gear 9 is reversed. The gear 49 is, therefore, driven out- Ward again from the center through the remainder of the operation and finally comes to rest at a position corresponding to (ct-Z7)2 which, of course, is the same position which would be occupied for (Zn-cl2. Since the counter I3 always reects the difference of position of the gears 42 and 49, the correct absolute value of the product will obviously be shown by the counter I3.

The mechanism may also be used for dealing with negative numbers and to this end the reversing clutch 40 is provided. The first effect oi' the backward turning of the handle I from zero will be to shift the clutch 40 to its upper position so that the gear 42 will be driven outward from the center of the spiral gear. From what has already been said with reference to the operating parts and with reference to the principle of operation it is thought that the manner in which the correct product is secured will be apparent and that a detailed analysis of the operation and of the principle of carrying it out will be unnecessary.

Briefly, however, the gear 42 always stands, when both handles I and 5 have been fully operated, at the position corresponding to the square of the algebraic sum of the quantities run in, and the gear 49 always stands at a position corresponding to the square of the algebraic difference of the quantities run in. The dinerential mechanism combines these operations so as to subtract the latter square from the former, and by a mere matter of gear ratios is caused to divide the difference by 4. The division, however, may, of course, occur farther back toward the source, and if it occurs in advance of the gears I and 9 the division will be by 2 instead of 4.

The reversing mechanism for the clutch 48 is driven from a bevel pinion 6I fast on the shaft 28. The pinion 6I drives a pinion 62 which is mounted on a drive shaft 63 of what may be an ordinary counter mechanism 64 of the Veeder type in which the number Wheels can be operated in either direction. This mechanism is not intended to give an information to the operator so that the numbers may be omitted and the wheels may be entirely enclosed. In fact, the gearing alone is important. For the purpose of making the principle of the reversing mechanism clear, however, it may be assumed that it consists of a counter comprising a series of decimal number wheels in which the sight opening would be at the side facing the observer in Fig. 1. The highest denomination wheel 65 is outside the capacity be a carry over to all wheels and the counter would read 9999. If it then operated forward one step it would` again read 0000. In other words, the wheel 65 operates from 0 to 9 when the counter goes backward from zero, and from 9 to 0 when the counter goes forward to zero. The wheel 65 has fixed upon it a clutch shifting fork 66 and from what has been said it will be apparent that the fork is shifted down when the counter 64 is operated backward from zero and is shifted up when the counter is operated forward to zero. The clutch includes pins 61 for engaging in recesses of the gear 4 and pins 68 for engaging in recesses of the gear 4a. Since the shift always occurs at exactly the same rotative position, alignment of the pins with the appropriate recesses is always assured.

The recesses are formed with flaring mouths to assist in guiding the pins. The pins enter the mouths of one set of recesses before leaving the mouths of the other set, so that faulty operation caused by overthrow or slight inaccuracies of timing is avoided.

The reversing mechanism for the clutch 40 may be substantially identical with the reversing mechanism for the clutch 48. This mechanism is driven from a pinion 69 fast on the shaft I9. The reversing mechanism may be assumed to be a counter exactly like the counter 64 but in which the sight opening would be on the side away from the observer in Fig. 1, so that if an observer went around to the far side and a sight opening were present he would see the units wheel at his right. As the device is viewed in Fig. l, however, the units Wheel is on the left and the direction of forward rotation is such that the tops of the Wheels travel toward the observer. The wheel of highest denomination has fast upon it a clutch shifting fork 'Ill.`

It will be apparent that the movement of the counter from 9999 to 0000 would carry the clutch fork 'I0 downward so that the down position is the positive position of the clutch 40. A change from 0000 to 9999 would carry the fork 'l0 upward so that the up position would be the nega'- tive position of the clutch 40.

The mechanism can obviously be used for division as well as for multiplication. This is done by first setting one of the counters 2 or 6, say 2, to show the known divisor, and then operating the other counter, 6, until the known dividend appears in counter I3. The quotient is then read from counter 6. l

A description of the construction and design of the squaring gears 1 and 9 has been left for last in order to avoid digressing from the exposition of the principle of operation of the apparatus.

The gears I and 9 are alike so that a description of one of them will apply to either. The diagram of Fig. 6 is marked as representing the gear-9 but applies equally to the gear 'I.

The primary requirement in constructing one of these gears is that the radius of the spiral shall increase in direct proportion tothe angle through which the gear is turned from zero. This is nec- -the form of studs set in holes armed in the face of the gear l.

A central'tooth would be bodily immovable and, therefore, would be meaningless since it would not move transversely of the axis of the spur gear and hence would impart no drive to the spur gear. It would simply be in the way and would impose unnecessary dimensional limitations upon the spacing of the crown gear teeth and the spiral gear teeth. Hence no central tooth is provided.

Any arbitrary distance from the center not greater than one quarter of the radial distance between adjacent turns of the spiral might be selected for the innermost tooth of the spiral. The radius of this innermost tooth stands at right angles to the direction of the axis of the spur gear in the zero position, and the spur gear is driven exclusively by this single tooth, desirably during approximately the first quarter turn of the spiral. This results in an output of some small quantity. Since the spiral must have the characteristic that its radius increases in direct proportion to the angle of rotation from zero, it is evident that if the radius of the first tooth is called K and this tooth represents 1/4 turn, then the radius'at 5/4 revolutions must be 5K-at, 9/4 revolutions, 9K-at 13/4 revolutions, 13K, etc. In other words the distance K of the first tooth from the center is 1A; of the distance between adjacent turns of the spiral.

Since the distance betweenadjacent turns of the spiral is uniformly equal to 4K, the crown gear can be, and desirably is, made thick enough to be engaged and guided by the teeth of the spiral turn next outside the turn with which the crown gear is in mesh.

It is desirable that the output during the first 1A turn shall approximate a square curve and that zero output shall occur at the zero position. During the rst 90 of revolution the movement of the innermost tooth transversely of the axis of the shaft 43 is proportional to l-cos c, (where c is the angle of displacement from zero) Since c l-cos' c=2 sinz the movement of the first tooth transversely of the axis of the crown gear is proportional to the square of the sine of 1/2 the angle of displacement from zero. The sine of an angle does not depart greatly from a straight line function of the value of the angle between 0 and 45. The transverse movement of the rst tooth does not, therefore, depart greatly in value from the square of the angle of rotation of the spiral gear.

It is a fact, however, that the angle increases more rapidly than the sine, that is, the slope of a sine curve diminishes somewhat as the angle increases. It should be noted, however, that the spiral gear tooth moves in the plane of a chord of the crown gear. The angle of rotation of the crown gear, therefore, is not directly proportional to the movement of the first spiral gear tooth transversely of the crown gear axis. On the contrary, the shaft 43 and the crown gear have their axes so related to the axis of the spiral gear that the rotation of the crown gearin relation to the movement of the first spiral gear tooth transversely of the crown gear axis is the reciprocal of a sine curve. This relation has a the spiral gear stands in the axial vertical plane of the crown gear and as it moves across the crown gear it moves away from the central vertical plane.

This displacement of the crown gear axis relative to the axis of the spiral gear has another important advantage. While the teeth after the rst tooth of the spiral gear travel in driving relation with the crown gear at both sides of its axial vertical plane, the driving travel on the left side of the vertical plane is relatively short as compared with the travel on the right side. Thus, assuming a uniform rate of rotation of the gear 'I the tendency of a pin is to accelerate the crown gear. This is particularly true because each spiral gear tooth of small radius moves into engagement with the crown gear through the face of the crown gear and with a substantial component of movement in the direction of the axis of the crown gear and a relatively slight component transversely of the crown gear axis, but leaves the crown gear through the periphery of the crown gear and at a time when the radius of the spiral gear tooth ,extends substantially parallel to the crown gear axis. The displacement of the crown gear axis has a further advantage in connection with the fact that the crown gear must at times be simultaneously engaged by two teeth of the spiral gear. The tooth of longer radius comes into engagement with the crown gear at a time when it has a substantial component of movement in the direction of the axis of the crown gear whereas the preceding tooth of shorter radius is at the same time moving more nearly at right angles to the axis of the crown gear. There is not, therefore, at any time any substantial disparity in the rates at which the two adjacent teeth tend to drive the crown gear.

For the purpose of constructing a spiral gear embodying the principle of the present invention the following formulas will be useful as a guide. Symbols used in the formulas have the followmg meanings:

P=diametral pitch of gear teeth.

T=tota1 number of gear teeth.

t=the number in the series of any specific tooth on the spiral pitch line, tooth No. 1 being nearest the center of the gear.

N--total number of revolutions of the gear.

R=radius of final tooth, i. e. the maximum radius of the spiral.

r=radius of tooth t.

c=angle of tooth t from the zero point on the spiral gear.

K=offset of first tooth and of the axis of the crown gear shaft 43 from the center of the spiral gear.

In designing the spiral gear the first step is to assume desired values for N and R.

' The mean radius of the spiral is The length of the spiral is 21rNR 2 The number of teeth for any diametral pitch can be obtained by dividing this last quantity by cR i- T-36'0'N-R\/ T Since the first derivative of a square function :ls a straight line function, r is proportional to the square root of K=r for the rst 90 of cam travel, therefore,

In the embodiment of Fig. 7 operators |0| and |02 are provided for running the multiplicand into a counter |03 and the multiplier into a counter |04. The operator |02 acts directly through a shaft |05 and a gear |06 upon a squaring gear |01 so that the input of gear |01 is equal to the multiplicand B and the output is equal to KB2 (K being a known constant). The operator |0| acts directly through a shaft |08 and a gear |09 upon a squaring gear I|0 so that the input of the gear I0 is equal to the multiplier A and the output is equal to KA2.

The shafts |05 and |08 are connected through differential gearing I|| to operate a squaring gear ||2 in the same direction so that the input of the gear ||2 is A+B and the output is K (A4-BW.

'Ihe gear |01 drives a gear I 3 which is fast with a pinion ||4 forming one element of the differential train while the gear I|0 drives a gear ||5 which is fast with a pinion IIB forming another element of the differential train. The pinions ||4 and ||6 mesh with pinions ||1 and |I8 which are carried by a spider I I9 fast upon a shaft |20. Rotation of the gear I I3 while the gear I I6 is stationary results in a turning of the shaft |20 in the same direction as gear I|3 but at one half the angular velocity. Similarly rotation of the pinion ||6 while the pinion ||4 is stationary results in rotation of the shaft |20 in the same direction as the pinion IIB but at one half the angular velocity. The reduction is compensated for by making output gear |2| of shaft |20 twice the diameter of the equal gears I I3 and I I5.

The output shafts |22 and |23 of gears |01 and ||0 are connected so as to cause their outputs to be added. The shaft |23 has fast upon it a spider |24 forming one element of a differential gear |26. The spider carries pinions |21 and |28 both of which are constantly in mesh with pinions |29 and |30. When the pinion |29 is stationary and the spider is turned by the shaft |23 the output gear |3| is rotated in the same direction as the shaft |23 but at twice the angular velocity. The shaft |22 has fast uponv it an output gear |32 which through two intermediate pinions |33 and |34 operates a gear |35. The gear |35 is fast with the pinion |29 but is rotatable upon the shaft |23. The gear |35 has a diameter equal to one half the diameter of the gear |32 so that the gear |35 has twice the angular velocity of the shaft |22. Rotation of the pinion |29 while the shaft |23 is stationary results in the turning of the gear |3| in the opposite direction to the gear |35 and at the same angular rate. Thus the combined effect of shafts |22 and |23 on the gear |3| is to cause the extent of operation of the gear |3| tol be 2K A2+B2 The gear |3| is connected through a pinion l|36 with a gear |31 of the same diameter as the gear |3|. The gear |31 is rotatably mounted upon the Output shaft 38 of the gear ||2. It has fast with it a pinion |39 forming one element of a differential gear |40. The differential gear comprises pinions |4| and |42 carried by a spider |43 which is fast upon the shaft |38. The pinions |4| and |42 mesh with the pinion |39 and with a pinion |44. The pinion I 44 is fast with an output gear |45. Rotation of the shaft |38 while the gear |31 is stationary results in rotation of the gear |45 in the same direction as the shaft |38 and at twice the angular rate. Thus the rotation of the shaft |31 through an angle corresponding to the value K(Ai-B)2 results in a rotation of the gear |45 through an angle corresponding to 2K(A+B)2. Rotation of the gear |31 while the spider |43 is stationary results in rotation of the gear |45 in the op posite direction to the gear 31 and at the same angular rate so that rotation of the gear |31 through an angle corresponding to 2K(A2+B2) results in a rotation of the gear |45 through an angle corresponding to -2K(A2+B2). The output of gear |45 is, therefore, equal to `Gears |46 and |41 for transmission of the output of gear |45 to a product indicator |41 are so chosen that the indicated product is equal to the output of gear |45 divided by 4K or AB.

In the form of the invention illustrated in Fig. 8 the multiplicand A is turned in 'by an operator 20| and the multiplier B is turned in by an operator 202. The multiplicand and the multiplier are indicated respectively upon counters 203 and 204. The multiplicand shaft 205 carries a gear 206 which drives gears 201 and 20B. 'I'he gear 201 is fast with a pinion 209 forming the element of a differential gear 2|0. The gears 201 and 209 are rotatably mounted upon a shaft 2||. A spider 2I2 is fast upon the shaft 2|| and carries rotatable pinions 2I3 and 2I4. The pinions 2I3 and 2I4 mesh with a pinion 2|5 which is journalled on the shaft 2I| and fast with a gear 2|6. When the gear 2I6 is stationary and the gear- 201 is rotated the spider turns in the same direction as the gear 201 but one half as fast as the gear 201 so that if the rotation of the shaft 205 is represented by 2A the rotation of the shaft 2|| will be represented by A. The shaft 2I| has fast upon it a gear 2|`| which drives a squaring gear 2|8.

The gear 2|6 meshes with a gear 2I9 which is journalledyupon Ia shaft 220 and which is fast with a pinion 22|. The pinion`22| forms an element of a differential gear 222. The shaft 220 has fast upon it a spider 223 which carries pinions 224v and 225, both in mesh with a pinion 226 which `is rotatably mounted upon the shaft 220 but which is fast with the gear 208. The rotation of the shaft 205 turns the pinion 226. At this time the pinion 22| is stationary and hence the shaft 220 is turned through the spider in the same direction as the gear 208 but at one half the angular speed so that, with an input of 2A from the shaft 205, the output of the shaft 220 will be A. The shaft 220 has fast upon it a gear 221 which through gears 228 and 229 operates a squaring gear 230. Operation of the handle 20| turns the vgears 2|8 and 230 to the same extent and in the same direction.

'Ihe operator 202 is fast upon a shaft 23| which shaft has fast upon it a gear 232 in mesh with a gear 233. The gear 233 is fast with the gear 2|9 but revoluble upon `the haft 220. When the operator 202 is rotated forward the gear 2|6 is driven at the same angular rate as the shaft 23|. Through the differential gearing 2|0, this results in rotation of the shaft 2|I at one half the angular'rate of the gear 2|6 but in the same direction as the gear 2|6. Since this direction of rotation, however, is opposite to that imparted to the gear 2|1 by operation of the handle 20| the resulting operation of the gear 2|8 will correspond to -B so that the net result of opera- .tion of the two handles 20| and 202 upon gear 2 |8 will correspond to A-B.

Rotation of the gear 2|9 will also act through the differential gearing 222 to turn the shaft 220 in the same direction as the gear 2 I9 but through one half the angular distance. This is the same eiiect produced upon the shaft 220 by the forward turning of the operator 20| so that the net eect of the two operators 20| and 202 upon gear 230 v will correspond to A+B.

In order to avoid the necessity for the reversing mechanism the follower 234 associated with the gear 2|8 is not started from the zero position but from a position on the gear track corresponding to Klc2. With the follower in this position, both of the counters 203 and 204, and also the product indicating counter 235, stand at zero. The effect of using this starting position is to avoid the possibility of the need for reversing mechanism regardless of Whether the larger or the smaller quantity is run in by the operator 202.

As a consequence of starting the follower 234 at the position Kk2 the follower is caused to travel from this position to a position corresponding to KUc-l-A-Blz when A-B is run into the gear 2|8. 'I'he output of `the gear 2|8 to the shaft 236 is, therefore,

In order to get K (A-B)2 from this output a quantity K [2km-BH must be subtracted from it. For the purpose of a subsequent combination of the difference with the output of gear 230, however, it is desirable that the subtrahend and the minuend be doubled so that the difference differential gear also comprises a spider 24|,

pinions 242 and 243 carried by the spider, and an output pinion 244. 'Gear 238 and the pinions 239 and 244 are rotatable upon a shaft 245, and the spider 24| is fast upon the shaft 245. The output pinion 244 has a gear 246 fast with it.

Since the peripheral travel of the gear 2|8 is proportional to A-B the rotation of shaft 245 may be made equal to K[2k(A-B)l merely by the proper selection of gearing. The shaft 245 is, therefore, driven from the gear 2|8 through a gear train of appropriate design. The train is illustrated as comprising a gear 241 driven by the gear 2|8, a bevel pinion 248 fast with the gear 241, and a bevel pinion 249 fast on the shaft 245 and driven by the pinion 248.

The input to the differential gear 240 of gear Rotation of the pinion 239 in the direction indicated by the arrow while the spider is held stationary will result in an equal and opposite rotation of the gear 246. Rotation of the shaft 245 in the direction indicated by the arrow while the pinion 239 is stationary will result in operation of thegear 246 in the same direction as the shaft 245 but throughtwice the angular distance. Thus the input of gear 238 and twice the input of shaft 245 are subtractively combined to form the output of gear 246. The output of gear 246 is, accordingly, 2K(A-B)2.

The output of gear 246 is transmitted through a gear 250 to gear 25|. The gear 25| is revolubly mounted upon the output shaft 252 of gear 230 and is fast with a pinion 253 which forms one element of a differential gear 254. The differential gear also comprises a spider 255 fast on the shaft 252, pinions 256 and 251 carried by the spider, and an output pinion 258 revolubly mounted upon the shaft 252. The pinion 258 has fast with it an output gear 259.

Rotation of the shaft 252 in the direction indicated by the arrow while the pinion 253 is held stationary results in rotation of the gear 259 .in the same direction as the shaft 252 but through twice the angular distance, so that if the angular input of shaft 252 is K(A|B)2 the revolution of gear 259 will be 2K(A+B)2. If the spider is held stationary while the gear 25| is rotated the gear 259 will be turned in the opposite direction to gear 25| but to the same angular extent as the gear so that the output will be -2K(AB)2 and this combined with the output caused by the rotation of the shaft 252 gives an output of SKAB. The gear 259 is connected to the product indicating counter 235 through a suitable gear train, shown as comprising gears 260 and 26|, for causing the factor 8K to be eliminated so that the product AB is indicated by the counter 235.

In the form of the invention disclosed in Fig. 9 both of the follower gears stand initially at the same position other than zero with respect to their associated squaring gears at the start and suitable compensation is provided for eliminating the error which would otherwise be produced by the false start. This form of device has the advantage that it is capable of handling either positive or negative inputs without the necessity of employing reversing mechanism.

An operating crank 30| mounted upon a shaft 302 is operated to run the multiplier into a counter 303, and an operating crank 304 mounted upon a shaft 305 is operated to run the multiplicand into a counter 306. Rotation of the crank 30| acts through differential trains 301 and 308 to run the multiplier A positively in the squaring gears 309 and 3I0. The input to the differential -geai's is from the shaft 302 through a pinion 3|| and thence, respectively, through pinions 3 I2 and 3|3. The output from the differential gear 301 is through a spider shaft 3|4 which is directly connected through a gear 3|5 to the gear 306. The output of differential gear 308 is through a spider shaft 3|6 which is connected through gears 3|1, 3|8 and 3|9 to drive the gear 3I0.

When the operator 304 is turned the input to differential gear 308 is through gears 320 and 32| the latter being revoluble upon the shaft 3|6. The input to differential gear 301 is through a gear 322 fast with the gear 32|, and through a gear 323 revolubly mounted upon the spider shaft 3|4.

The follower 324 associated with the squaring gear 309 stands at a position corresponding to Klc2 when the counters 303 and 306 stand at zero. At this time the product indicating counter 325 also stands at zero. The follower gear 326 stands at a position corresponding to Kk2 on its squaring gear 3I0 at the time when the counters all stand at zero. When the gear 309 has been operated to the extent of A-B the follower gear will have been moved from the position corresponding to Klc2 to the position corresponding to K(1c+A-B)2 so that the output of the shaft 321 upon which the gear 324 is mounted will be proportional to the difference between the starting and final positions; that is,

Similarly, the output of shaft 328 upon which the follower gear 326 is mounted will be Differentially combining these two outputs would yield as a result 4KAB-4KkB. The rst term is obviously wanted and the second unwanted. Provision is accordingly made for adding 4KkB to the output of shaft 321 and then subtracting the resulting sum from the output of shaft 328. The preceding sentence is correct in principle but is not quite accurate as related to the illustrative apparatus, for the reason, as will become apparent, that the output of 328 is multiplied by two and hence provision is made for multiplying the output of shaft 321 by two and for making the compensation twice as great as that stated above.

The shaft 321 has fast upon it a gear 328 which drives a gear 330 at twice its own angular speed. The gear 330 is fast with a pinion 33| and is revoluble upon a shaft 332. The pinion 33| forms one element of a differential gear 333. The differential gear also comprises a spider 334 fast upon the shaft 332, pinions 335 and 336 carried by the spider; and an output; pinion 331 revoluble upon the shaft 332. The output pinion 331 has an output gear 338 fast with it.

The gear 323 which is driven only from the operator 304, and therefore in proportion to the quantity B, is connected through a gear 338 a shaft 340 and bevel pinions 34| and 342 to drive the shaft 332. Since the gear 323 is operated in proportion to the quantity B it is evident that the output of the shaft 332 may be made equal to 4KkB by appropriate selection of gearing.

When the shaft 332 is turned and the pinion 33|` is idle, the gear 338 is driven in the same direction as the shaft 332 but through twice the angular distance so that the output is BKkB. When shaft 332 is stationary and the gear 330 is driven in the direction indicated by the arrow the gear 338 will be driven in the opposite direction but to the same extent as the gear 330 is driven. Both rotations of the gear 33B are in the same direction, so that the inputs are additively combined, and thus the output of gear 338 is caused to be This output is transmitted through gear 343 to a gear 344 which is revoluble upon the shaft 328 and fast with a pinion 345. The pinion 345 forms one element of a differential gear 346. The differential gear also comprises a spider 341 fast on the shaft 328, pinions 348 and 349A carried by the spider, and an output pinion 350 which is revoluble upon the shaft 328. The output pinion 350 has fast with it an output gear 35|. When the shaft 328 ls rotated in the direction indicated by the arrow the output gear 35| is rotated in the same direction and to twice the angular extent. When the gear 344 is rotated and the shaft 328 is stationary the gear 35| is rotated to the same angular extent as the gear 344 but in the opposite direction. Thus, the output of gear 344 is differentially combined with twice the output of shaft 328 giving as a result SKAB. The gear 35| is connected through a suitable gear train to operate the counter 325, the gears being so chosen that the factor 8K is eliminated and the counter 325 iscaused to correctly indicate the product AB. 'I'he gear train is illustrated as comprising gears 352 and 353.

Fig. 10 is a diagrammatic view illustrating how a machine constructed inaccordance with the principle of the machine in Fig. 1 may be utilized to advantage where one of the quantities to be multiplied is known to have a minimum limit other than zero. In this figure the A counter, 40|, is indicated as covering a range from zero to 1000, and a B counter, 402, is indicated as covering a range from 400 to 1400. When the A counter is at zero and the B counter is at 400 the followers of both squaring gears stand at zero. The input to one side of the multiplier is A and the input to the other side is B-400. One of the squaring gears of the multiplier 403 has an input of B-400-i-A and an output of (B-400-i-A) 2, while the other has an input of B-400-A and an output of (B-400-AV2. The difference of the outputs is 4A(B-400). It is apparent that the desired product AB can be obtained from this formulae by adding 1600A and then dividing the sum by 4. Provision is accordingly made of gearing 404, operated from the A train 405, to produce an output of 1600A which, through differential gearing 406, is added to the output of the multiplier 403 to produce an output 4AB. The factor 4 is eliminated through transmission gearing 401, with the result that the product indicating counter 408 is caused to indicate the product AB correctly. In the diagram the input from the A operator is indicated as transmitted by a train 405 to diierential gearing 409, and the input from the B operator is indicated as transmitted by train 4|0 to differential gearing 4| The differential gears are combined, in fact, as in Fig. l. The gearing for operating the gear that squares the sum is indicated by the line M2, and the gearing for operating the gear that squares the diierence is indicated at M3. The output gearing of the multiplier, after the squares of the sum and the difference have been combined, is indicated at 6M.

We have described what we believe to be\the best embodiments of our invention. We do not wish, however, to be confined to the embodiments shown, but what we desire to cover by Letters Patent `is set forth in the appended claims.

We claim:

1. In a multiplying machine, in combination, means for running in a multiplicand, means for running in a multiplier, operating trains effective respectively to combine the multiplier andthe multiplicand additively and subtractively, means including flat spiral squaring gears oper' able respectively in proportion to the sum and the difference of the multiplier and the multiplicand, means comprising crown gears operable by the respective spiral gears in proportion to the square of the sum and the square of the diierence of the multiplier and multiplicand, and means operable in proportion to the difference of operation of the last mentioned means to indicate the product.

2. In a multiplying machine,l in combination, means for running in a multiplicand, means for running in a multiplier, a train operable in proportion to the sum of the multiplicand and the multiplier, a train operable in proportion to the difference of the multiplicand and the multiplier, gearing including a flat spiral gear operable by the first train for producing an output in proportion to the square of the sum, gearing including a at spiral gear operable by the second train for producing an output in proportion to the square of the difference, a product indicator, and means operating said indicator in proportion to the diierence of the outputs of said gearings.

3. In a multiplying machine, means for running in a multiplicand and a multiplier, a pair of output devices responsive to the running in of the multiplicand and the multiplier, one including means for producing an output proportional to the square of the sum of the multiplier and the multiplicand and the other including means for producing an output proportional to the square of the difference of the multiplier and muliplicand. a product indicator, and indicator operating means responsive to said output devices to combine the outputs differentially so that the indicator remains idle during operation of the output devices in unison but operates proportionally to any diierence of operation of the two output de- VICES.

4. In a multiplying machine for obtaining the productI of two numbers from the difference of the squares of their sum and difference, in combination, means for separately running in the numbers, a sum train responsive to the running in of the numbers and including means for producing an output proportional to the sum of the numbers, a difference train responsive to the running in of the numbers and including means for producng an output proportional to the diierence of the numbers, squaring gears operated respectively by the sum and difference trains and means including a control device operated by the difference train for reversing the direction of drive of the diierence train output when the total operation of the difference train passes through zero.

5. In a multiplying machine for obtaining the product of two numbers from the difference o! the squares of their sum and difference, in combination, means for separately running in the numbers, a sum train connected to be similarly responsive to the running in of the numbers and including means for producing an output proportional to the sum of the numbers, a difference train connected to be oppositely responsive to the running in of the numbers and including means for producing an output proportional to the difference of the numbers, squaring gears operated respectively by the sum and diierence trains, and means including a control device operated by the diieernce train for reversing the drive of either train upon the total operation of the diiierence train passing through zero.

6. In a multiplying machine, the combination with two squaring gears, vof associated follower gears, one of which starts from zero and the other of which starts from a predetermined point other than zero, means for running in the multiplicand and the multiplier, and means including multiplying gearing controlled by the magnitude of the difference between the multiplicand and the multiplier for producing an output which is a linear function of such difference, and differential gearing for combining such output with the outputs of the squaring gears, to compensate for the fact that one of the squaring gear followers did not start from zero.

7. In a multiplying machine, the combination with two squaring gears, of associated follower gears both of which start from the same predetermined position other than zero, meansfor running in the multiplicand and the multiplier,

and means including multiplying gearing controlled by the magnitude of the multiplier for producing an output which is a linear function of the multiplier, the dierential gearing for combining such output with the outputs ofthe squaring gears to compensate for the fact that the squaring gear followers did not start from zero.

8. A computing machine comprising, in combination, input means whose input may be'either positive or negative, a squaring gear, output means driven by the squaring gear in proportion to the square of the input, a driving train from the input means to the squaring gear, including alternative connections between the input means and the squaring gear of opposite, eect for changing the relative direction of the drive, and means including a control device operated by the driving train connections each time that the net value of the input passes through zero, whereby the squaring gear is caused always to be operated in a positive direction in proportion to the departure of the input value from zero, and the output of the squaring gear is caused always to be positive regardless of the sign of the input.

9. A computing machine as set. forth in claim 8 in which the control device comprises a clutch member shiftable between the alternative driving connections, denomination gears and carryover gears operable directly by the driving train in either direction, and a clutch shifting member carried by the gear of highest denomination, the gear of highest denomination being outside the capacity of the machine and, therefore, operable only when the driving train pases through zero.

10. A computing machine having, in combination, revoluble multiplicand input means,'regis ter means directly responsive to said input means for showing the instantaneous values of the muluct indicating .means are geared together for causing the product indicating means,` in response to the joint eiect of the multiplier and muitiplieand input means to show the instantaneous values of the product continuously as the product changes in value.

`" WILLIAM L. MAXSON.

PETER J. MCLAREN.

CERTIFICATE OF CO RRECTI ON a Patent No 2, 191i, LL?? WILLIAM L. MAxsoN, ET AL.

March 26, 19110.

It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: Page 9, second column, line 59, claim?, for "the differential" read and differential;

and that the said Letters Patent should be read with this correction ltherein that the samemay conform to the record of the case in the Patent Office.A

Signed and sealed this 50th day of April, A. D. l9li0.

(Seal) Henry Van Arsdale, Acting. Commissioner of' Patents.

CERTIFICATE OF CORRECTION;

patent No. 2,19h,h77. March 26, 19Llo.

WILLIAM L. MAXSON,1 ET AL.

It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: Page 9, second column, line 59, claim?, for the differential" read and differential;

and that the said Letters Patent should be readwith this correction therein that the samemay conform to the record of the case in the Patent Office.-

signed and sealed this 50th day of April, A. D. 19140.

Henry Van Arsdale,

(Seal) Acting. Commissioner of Patents. 

